JPH0250358B2 - - Google Patents

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention provides a lubricating device for a piston-cylinder assembly,
Specifically, it has at least one piston-cylinder assembly forming a pulsating chamber, and in particular has a retractable sealing tube that is slidably supported on the inner surface of the cylinder via lubricating oil, and is adapted to the vertical movement of the piston. The present invention therefore relates to a lubricating device for a piston/cylinder assembly which forms a pulsating chamber in the sealing tube.

(Prior art and its problems) In the piston/cylinder assembly described above, lubricating oil is supplied to the sliding surface between the piston and the cylinder, or to the sliding surface between the tube and the cylinder in the case of an assembly having a sealing tube. Requires a lubrication system including a forced circulation lubrication system.

However, the above-mentioned lubricating device includes a lubricating oil chamber (oil tank) that stores lubricating oil, an oil supply pump that supplies lubricating oil from the oil chamber to the assembly, a recovery chamber into which lubricating oil that has acted on the cylinder assembly is introduced, and recovery. It is necessary to be equipped with a reflux pump that returns lubricating oil from the chamber to the oil chamber, but in conventional devices, the lubricating oil chamber, oil supply pump, etc. are arranged separately from the housing of the piston-cylinder assembly. It is connected, especially the lubricating oil chamber,
The fuel pump was designed to be placed in an obvious manner in relation to the assembly. Therefore, in conventional equipment, the positions of the assembly, lubricating oil chamber, and oil supply pump are far apart, making the overall size larger, and the layout of the circulation oil supply system connecting each member becomes complicated, with some parts exposed. This is not desirable.

In addition, in the case of a lubricating system, it is effective to include a lubricating oil cooling device in the circulation oil supply system to improve the operational stability of the device and the performance of the piston/cylinder assembly, but the location of the cooling device Depending on the configuration, the device becomes even larger and more complex, resulting in a significant increase in manufacturing costs.

In view of the conventional circumstances, the present invention provides a lubricating device for a piston-cylinder assembly, which allows each member of the lubricating device to fit well, making the device compact and reducing manufacturing costs. This is what I am trying to do.

(Means for Solving the Problems) Means for solving the problems of the present invention include at least one piston-cylinder assembly forming a pulsating chamber, a lubricating oil chamber containing lubricating oil, and a lubricating oil chamber containing lubricating oil. A closed circuit including an oil supply pump that supplies lubricating oil from a chamber to the piston/cylinder assembly, a recovery chamber into which the lubricating oil that has acted on the piston/cylinder assembly is introduced, and a return pump that returns the lubricating oil from the recovery chamber to the oil chamber. a forced circulation oil supply system consisting of the lubricating oil chamber;
The refueling pump, recovery chamber and reflux pump are pistons and
The lubricating oil chamber is formed in a housing common to the cylinder assembly, and has an annular shape that surrounds and is concentric with the axis of rotation of the drive device of the assembly.

Further, it is preferable that the oil supply pump and the return pump are also arranged concentrically with the axis of the drive circuit of the piston-cylinder assembly, and the oil supply pump is arranged there using the annular inner space of the lubricating oil chamber. This is preferable since it can be further miniaturized.

Means for solving the problems related to the cooling device of the present invention is that a heat exchanger is arranged in the lubricating oil chamber, and a part of the working medium is supplied by a working medium supply means that supplies the working medium to the assembly. The lubricating oil in the lubricating oil chamber is cooled by sending the lubricating oil through the heat exchanger.

The working medium supply means includes, for example, a supply pump (axial flow pump), and this supply pump supplies the working medium (for example, oil, but it is distinguished from the lubricating oil) into the cylinder of the piston-cylinder assembly. A portion of it is supplied to the heat exchanger as a bypass and used for cooling the lubricating oil.

The heat exchanger connects the working medium inflow side to the outflow side of the supply pump, so that the working medium,
It is preferred that a very strong heat exchange takes place between the lubricating oils and that the working medium line of the heat exchanger is configured as a reflux bypass connecting the outflow side and the inflow side of the supply pump.

Further, the supply pump also utilizes the annular inner space of the lubricating oil chamber, and by arranging it there, it is possible to further downsize the apparatus.

(Function) According to the present invention, the lubricating oil chamber, the oil supply pump, the recovery chamber, and the reflux pump that constitute the lubricating device are formed within the housing of the piston/cylinder assembly, and the circulation oil supply path between these members is connected to the housing. It can be distributed within the body.

In addition, the arrangement position of the lubricating oil chamber allows the assembly and the lubricating oil chamber to be brought close to each other, thereby reducing the size of the casing, and the annular shape of the lubricating oil chamber allows for the use of the annular internal space. The oil supply pump or means for supplying a working medium to the assembly (oil supply pump)
, and to improve the fit of these parts and reduce the installation space.

Furthermore, by interposing the overflow channel between the lubricating oil chamber and the recovery chamber, the recovery chamber is always kept filled with lubricating oil, and air bubbles in the lubricating oil are returned to the lubricating oil chamber via the reflux pump. to prevent it from getting caught.

In addition, in a lubricating device equipped with a cooling device,
A portion of the working medium supplied to the piston-cylinder assembly by the working medium supply means detours to the heat exchanger in the lubricating oil chamber and cools the lubricating oil in the oil chamber.

Since the heat exchanger is disposed within the lubricating oil chamber, the device can be easily accommodated even with the provision of a cooling device, and the external space of the casing is not expanded.

(Example) To explain an example of the present invention with reference to the drawings, the first example is as follows.
In the figure, 10 is a drive device, and 12 is a positive displacement main pump. , that is, the slider 3 has a number of pressing surfaces 4 corresponding to the number of pumps 12, and the main pump 12
is a piston-cylinder assembly composed of a piston 20, a sealing tube 22, and a cylinder 25.

The main pump 12 has a star-shaped multi-cylinder structure in which a plurality of the main pumps 12 are arranged facing the pressing surface 4 on the outer periphery of the rotary cam 2, and each main pump 12 has a star-shaped multi-cylinder structure.
The plunger 30 engages with the bottom of the piston 20 and surrounds the outer periphery of the cylinder 25, and is interlocked with the pressing surface 4 of the drive device 10.

The main pump 12 has a sealing tube 22 having a high elasticity and is made of rubber, for example, and is formed into a tube shape, and its upper end is connected to a cylinder 25.
The upper end of the sealing tube 22 is connected to the piston 20, and the lower end thereof is connected to the piston 20, thereby forming a working chamber 24 within the sealing tube 22.

Therefore, in the main pump 12, as the piston 20 moves up and down via the pressing surface 4 and the plunger 30 as the rotary cam 2 rotates, the sealing tube 22 expands and contracts in the axial direction within the cylinder 25. The internal volume of the working chamber 24 in the
This creates an expanding pulsating action which causes cylinder 2
5 a check valve 26 provided in a flow path 28 communicating with the upper end;
27 to perform a pumping action.

That is, during the expansion stroke of the working chamber 24 when the piston 20 descends, the check valve 26 opens and the check valve 2
7 closes to suck the working medium (for example, oil) into the working chamber 24 from the inflow side of the flow path 28, and during the contraction stroke in which the piston 20 rises, the check valve 26 closes and the check valve 27 opens to operate. The working medium sucked into the chamber 24 is discharged to the outflow side of the flow path 28.

In the working chamber 24, a spring 23 for biasing the piston 20 downward is interposed between the upper wall of the cylinder 25 and the piston 20.
and press the bottom portion 30b against the pressing surface 4 of the drive device 10.

The plunger 30 has a shape consisting of a bottom part 30b interposed between the piston 20 and the pressing surface 4, and a cylindrical part 30a extending upward from the outer periphery of the bottom part 30b. A space is formed between the inner surface of the cylindrical portion 30a and the outer surface of the cylinder 25, thereby forming an annular throttle flow path 45.

In addition, the inner surface of the cylinder 25 and the sealing tube 2
2. In order to reduce sliding friction with the outer surface of the cylinder, lubricating oil is supplied through the supply port 90b to the upper part of the passage 25a formed between the two, and the supplied lubricating oil flows down the passage 25a and flows into the cylinder. 25 located at the lower end of the passageway 25a, the relatively low pressure passageway 42
leading to.

The lower end of the cylinder 25 is open, so that the throttle passage 45 communicates with the chamber 42 between the intermediate passages 25a, and the upper end of the throttle passage 45 is connected to the cylindrical portion 3.
It communicates with a side chamber 35 formed at the upper end of the cylinder 25, that is, at the outer periphery of the cylinder 25.

Further, in FIG. 1, a reflux pump 105 is attached to the main shaft 1 at a position adjacent to the cam 2, and a lubricating oil supply pump 100 and a working medium supply pump 150 are respectively disposed in close proximity to the sides thereof. A recovery chamber 120 is formed on the outer periphery of the cam 2, and an annular lubricating oil chamber 110 is formed on the outer periphery of the supply pump 150 concentrically with the axis XX of the main shaft 1, and these members 105, 100, 150, 12
0, 110 and the main pump 12 described above are all assembled into a housing surrounding the outer periphery of the main shaft 1.

The supply pump 150 is an axial flow pump that feeds a working medium, that is, a liquid such as oil or water into the working chamber 24 of the main pump 12 described above, and its discharge side 151 is connected to the It communicates with the flow path 28.

The flow path 28 is an annular path leading to the outflow side 151 , and the flow path 154 extends horizontally from the annular flow path 152 toward each main pump 12 , and connects its tip to the flow path 28 of each main pump 12 . It is communicated by passage 156. On the inflow side 157 of the supply pump 150,
A working medium inlet 158 is connected.

Therefore, the inflow side 157 via the inflow port 158
The working medium that has entered is supplied from the outlet side 151 to the flow path 156 via the flow paths 152 and 154 by driving the supply pump 150, and the check valve 26 is opened in conjunction with the operation of the main pump 12. When the working medium is sucked into the working chamber 24 of the main pump 12 through the flow path 28 (when the check valve 27 is in the closed state), when the working chamber 24 enters the contraction stroke, the check valve 26 closes. When the valve is closed and the check valve 27 is opened, the working medium in the working chamber 24 is discharged to the outflow side of the flow path 28 and supplied to a predetermined location outside the housing.

On the other hand, the oil supply pump 100, the recovery chamber 120, and the reflux pump 105 constitute a forced lubricating oil circulation system consisting of a closed circuit that supplies the lubricating oil in the lubricating oil chamber 110 to the sliding surface of the main pump 12.

By arranging the lubricating oil chamber 110 as described above, the communication passages to the plurality of main pumps 12 are arranged at predetermined intervals on the circumference and at equal distances, and the arrangement of the communication passages becomes easy. .

The forced oil supply pump 100 sucks lubricating oil from a lubricating oil chamber 110 through an inflow passage 103, sends it to a filter 102 through an outflow passage 104, and further supplies it to an annular distribution passage 101. The lubricating oil is transferred from the distribution channel 101 to the pressure channel 9 including the adjusting throttles 90a and 95a, respectively.
0.95 to reach the individual main pumps 12.

The lubricating oil from the flow path 90 to the main pump 12 is supplied to the intermediate passage 25a through the supply port 90b of the cylinder 25, lubricates between the cylinder 25 and the sealing tube 22, and flows into the intermediate chamber 42. do.

During this period, the chamber 42 generates a pulsating action due to the vertical movement of the piston 20, and the pressure in the chamber 42 becomes relatively low during the upward stroke of the piston 20, so that the pressure in the chamber 42 is relatively low.
The lubricating oil in a is allowed to flow out into the spacer chamber 42 without any hindrance,
During the downward stroke of the piston 20, the lubricating oil that can flow down into the side chamber 42 passes through the throttle channel 45 and flows into the side chamber 3.
Discharge to 5.

Further, in order to reliably feed lubricating oil from the intermediate chamber 42 to the side chamber 35, low pressure must also exist in the side chamber 35.

For this purpose, the side chamber 35 is communicated with the lubricating oil chamber 110 via a balanced flow path 40 having a large opening cross-sectional area. This lubricating oil chamber 110 has a large internal volume and is maintained in a pressure-released state.

On the other hand, the lubricating oil supplied through the flow path 95 is
It is supplied between the outer surface of the cylindrical portion 30a of the plunger 30 and the guide surface 48 with which it slides, smoothing the sliding movement of the outer surface of the cylindrical portion 30a that moves up and down together with the piston 20.

The lubricating oil flows down to the pressing surface 4 through the flow path 47 and further flows into the recovery chamber 120.

The reflux pump 105 absorbs the lubricating oil recovered from the lower part of the recovery chamber 120 via the flow path 115, and supplies it to the top portion 110a of the lubricating oil chamber 110 via the rising reflux flow path 106.

The end of the flow path 115 on the side of the recovery chamber 120 is always located below the surface of the lubricating oil accumulated in the chamber, thereby preventing air bubbles from being drawn in when the reflux pump 105 sucks the oil and causing it to flow into the lubricating oil chamber 110. Make sure that there are no air bubbles in the lubricating oil.

In addition, in order to reliably prevent the empty suction of the reflux pump 105 and the entrainment of air bubbles, the recovery chamber 12
An overflow channel 130 connecting the lower part of the 0 and the lubricating oil chamber 110 is connected, and lubricating oil is supplied into the recovery chamber 120 through the channel 130, so that a predetermined amount of lubricating oil is always stored in the recovery chamber 120. Make it so.

Further, in order to prevent an excessive amount of lubricating oil from flowing into the recovery chamber 120, an inflow amount adjusting member is provided.

This adjusting member is a freely adjustable throttle valve 135.
It is sufficient to simply provide a in the flow path 130. However, in the illustrated embodiment, an overflow adjustment mechanism is provided which includes a controllable valve 135 as the adjustment member and a float 140 as the adjustment device. Thereby, the inside of the recovery chamber 120 can be maintained at an appropriate amount of oil.

It is essential to always maintain an appropriate amount of lubricating oil in the recovery chamber 120, and therefore to eliminate idle suction from the reflux pump 105, in order to prevent the inclusion of air bubbles that will have a negative impact on reliable forced circulation lubrication. be.

FIG. 2 is a configuration diagram showing the forced circulation oil supply system of the pump, and the main members are given the same reference numbers as in FIG. 1.

That is, the lubricating oil in the lubricating oil chamber 110 is sent to the filter 102 via the flow channels 103 and 104 by the drive of the oil supply pump 100, and then is sent from the annular distribution channel 101 to the main pump 12 via the pressure channels 90 and 95. is supplied to each sliding surface around the cylinder 25 and piston 20.

The lubricating oil used for lubrication around the cylinder 25 and piston 20 is then collected into the recovery chamber 120, and some of the lubricating oil that has reached the side chamber 35 is passed through the equilibrium flow path 40. Lubricating oil chamber 1
Return to 10.

The lubricating oil recovered into the recovery chamber 120 is returned to the lubricating oil chamber 110 via the channels 115 and 106 by the operation of the reflux pump 105.

In addition, FIG. 2 also shows the above-mentioned overflow passage 130, and also shows an outflow passage 109c for returning the lubricating oil containing bubbles from the reflux pump 105 to the recovery chamber 120, which will be described later.

As already mentioned, the prevention of air bubbles in forced circulation lubrication systems is essential to reliable functionality. Reflux pump 10 as shown in Figures 3 and 4
This condition is satisfied by forming slits as a plurality of reservoir holes 105b arranged in a radial centrifugal pump type in the rotor 105a of No. 5 and extending in a direction shifted from the radial direction of the pump rotation axis XX. The lubricating oil in this reservoir hole 105b is subjected to a strong centrifugal force as the rotor 105a rotates, and a large or small amount of liquid in the lubricating oil and a small or large amount of gas or bubbles accumulate in the lubricating oil. The air bubbles are separated within the hole 105b.
When discharged from the reservoir hole 105b, the liquid component flows out first, followed by the bubble component being discharged later.

Therefore, by arranging the two outflow control ports 108 and 109b on the outer periphery of the rotor 105a, one behind the other in the rotational direction within a circumferential angle of 180 degrees or less, the reservoir hole 105b first faces the control port 108. During the passage, only a very small amount of the lubricating oil containing gas or bubbles is released into the control port 108 and returned to the lubricating oil chamber 110 via the flow path 106 .

Next, when the reservoir hole 105b communicates with the control port 109b, a portion of the lubricating oil remaining in the hole 105b containing a large amount of gas or bubbles is discharged to the control port 109b and flows out into an outflow path 109c (not shown in FIG. 1).
is returned to the collection chamber 120 via.

As is clear from FIG. 3, the outflow control port 108
and 109b are set within a range of 180 degrees or less, and in other ranges, the outer end of the reservoir hole 105b is closed by the inner surface 107 of the housing, so new lubricating oil is added to the reservoir hole 105b while rotating in this section The reservoir hole 105b is closed because there is no inflow of
The lubricating oil is effectively separated from the bubble components within.

FIG. 4 shows another modification useful for gas or bubble separation within the rotor of reflux pump 105. Although this modification is shown in an enlarged view, in a section where the outer end of the reservoir hole 105b is closed to the inner surface 107 of the housing, a relatively wide space is formed so that the side openings of the hole 105b face each other. 〓109a
Form it.

As a result, while the reservoir hole 105b accommodates the lubricating oil and rotates, the centrifugal force accompanying the rotation of the rotor and the oil flow in the hole cause a radial circulation flow that follows course A to flow between the hole 105b and the hole 105b. It is generated within 109a. As a result, the reservoir hole 105
As for the lubricating oil in the hole (b), a large amount of oil containing few bubbles gathers in the radially outer region of the hole, thereby promoting the separation action.

Further, the gap 109a is communicated with the flow path 109c, and the air bubbles accumulated in the radially inner area of the accumulation hole 105b are collected through the flow paths 109a and 109c or through another flow path instead of the flow path 109c. Room 1
It is also possible to return it to 20.

FIGS. 5 and 6 show another embodiment of the present invention, in which a lubricating oil cooling device 200 is provided within the annular lubricating oil chamber 110 described above.

In this cooling device 200, a part of the working medium introduced into the supply pump 150 is connected to a flow path system 212 shown in FIG.
The main component is a heat exchanger 210 having:

The supply pump 150 is installed in a pump chamber 140 that is formed concentrically inside the lubricating oil chamber 110, and the opening side end surface of the chamber 140 is closed by a cover 232.
The side end cover surface 155 of the housing is formed by the end wall 230 that closes the end face 155 of the housing.

The cover 232 is formed with an inlet 171 through which the working medium is introduced into the pump chamber 140.

As shown in FIG. 5, the supply pump 150 is an axial flow type with its rotor attached to the tip of the main shaft 1 that can protrude into the pump chamber 140, with an inlet side 160 on the front side and an outlet side 170 on the back side. Configured as a pump, the outlet side 170 has a radially extending flow channel 17
2 to the annular flow path 174.

This annular flow path 174 communicates with a plurality of branch flow paths 176 (only one is shown in FIG. 5) extending in the axial direction, and the working medium is supplied to each of the main pumps 12 described above through each branch flow path 176. They are connected to a flow path 28 (FIG. 1) leading to the main pump 12 for supply.

With this configuration, each main pump 12 is supplied with a working medium that is appropriately pressurized, for example, at a flow pressure of several atmospheres, by the supply pump 150, and when the piston 20 descends (suction stroke), the working medium is is reliably filled into the working chamber 24.

Further, a flow path portion 178 extending rearward of the branch flow path 176 is communicated with an annular flow path 180 formed in the cover 232, and is connected to the outlet side 1 of the supply pump 150.
A portion of the working medium supplied from 70 to branch channel 176 flows into annular channel 180 via channel section 178 .

Radial flow path 18 starting from annular flow path 180
2 is inserted into and supported by the end wall 230 of the heat exchanger 21
0 inlet flow distributor 216 has been reached. A partial flow of the refrigerating medium branched from the pump chamber outlet side 170 of the supply pump 150 is transferred from an inlet flow distributor provided at the lower end of the lubricating oil chamber 110 to the heat exchanger 210 shown in FIG. A discharge flow collector 2 is provided at the top end of the lubricating oil chamber 110 via the flow passage system 212, that is, at a position facing the introduction flow distributor 216 across the diameter.
It reaches 18. This discharge flow collector 218 is also inserted and supported on the outside of the end wall 230. The discharge flow collector 218 communicates with the inlet side 160 of the pump chamber 140 via a radial passage 184 .

Therefore, the working fluid supply line by the supply pump 150 is supplied to the heat exchanger 210 in addition to the main supply passage that supplies the inlet side of the main pump 12, and is then returned to the inlet side 160 of the pump chamber 140. A reflux circuit is formed.

In order to properly maintain the supply amount and supply pressure to the main supply path, means is provided to adjust the supply amount of the working medium to the reflux circuit.

That is, the tip of the end wall 230 is connected to the flow path 1.
A throttle screw 220 that can be retracted and retracted is installed in 82, and the amount of branched supply to the introduced flow distributor 216 can be adjusted by adjusting the screw 220.

The details of the structure of the heat exchanger 210 are shown in FIG. As is clear from the figure, the flow path system 212 of the heat exchanger is almost completely immersed within the lubricating oil chamber 110 and below the lubricating oil liquid level. Lubricating oil reflux pump 105
The return passage 106 is located at the top end 110 of the lubricating oil chamber 110.
a and is sucked into the lower end by the forced oil supply pump 100, so a lubricating oil flow is generated in the replenishment chamber 110 that flows from the top end downward in substantially both circumferential directions toward the lower end. This lubricating oil flow is in the opposite direction to the working oil flow in the flow system of heat exchanger 210 found between the lower inlet flow distributor 216 and the upper discharge flow collector 218. That is, since countercurrent heat transfer occurs between the lubricating oil flow in the lubricating oil chamber 110 and the working medium flow in the heat exchanger 210 flow path system, the lubricating oil is strengthened by the newly flowing working medium. cooled down.

The flow passage system 212 of the heat exchanger 210 is constituted by a plurality of annular heat exchange elements 214 extending in the circumferential direction within the lubricating oil chamber 110, and these elements 214 are connected to the lubricating oil level within the lubricating oil chamber 110 as described above. The entire surface of the lubricating oil allows for heat exchange with the lubricating oil.

The heat exchange element 214 is formed in an arc shape along the annular shape inside the lubricating oil chamber 110, and is connected to an inlet flow distributor 216 and a discharge flow distributor 2.
18, and a plurality of them (three in the drawings of the embodiment) are arranged in parallel at intervals in the front and rear.

Thus, heat exchangers are formed which are arranged in a generally cylindrical manner in the direction of the cylinder axis, ie, a heat exchange surface with a large area adapted to the spatial relationship of the lubricating oil chamber and the lubricating oil flow.

Further, by arranging the heat exchanger 210 within the lubricating oil chamber 110, space can be used more effectively and the casing can be made smaller than in a structure in which the heat exchanger 210 is separately disposed outside the lubricating oil chamber.

Furthermore, by configuring the lubricating oil chamber 110 in an annular shape, not only does it take up less space when it is incorporated into the overall structure of the device housing, but also the lubricating oil can flow from the top to the bottom along the annular shape of the lubricating oil chamber. The cooling effect of the lubricating oil can be enhanced by forming a flow of the cooling fluid from the lower part upward in the opposite direction.

(Effects) According to the present invention, as described above, the lubricating oil chamber, the oil supply pump, the recovery chamber, and the reflux pump of the lubricating device are arranged so that they fit well within the casing of the piston-cylinder assembly, and the outer shape of the casing The space can be reduced and the device can be made more compact, and the oil path between each of the members can also be easily routed within the casing, causing the oil path to be exposed outside the casing and become an obstacle. No inconvenience.

In addition, by preventing air bubbles from being trapped in the lubricating oil that is returned to the lubricating oil chamber, the lubricating oil that is supplied to the sliding surfaces of the piston-cylinder assembly is free of air bubbles and its lubrication performance is improved. It is possible to maintain

Furthermore, even in lubricating systems equipped with a cooling system, compared to conventional systems in which a cooling system including a heat exchanger is placed separately outside the lubricating oil chamber, and outside air (refrigerant) is fed into the heat exchanger using a cooling fan, the piston - The size can be significantly reduced by using the working medium supplied to the cylinder assembly and arranging the heat exchanger in the oil chamber.

[Brief explanation of the drawing]

FIG. 1 is an axial cross-sectional view of a star-shaped multi-cylinder reciprocating pump including an eccentric wheel drive device, FIG. 2 is a flow path configuration diagram showing the oil supply system of the pump shown in FIG. 1, and FIG. The figure is an enlarged view of the reflux pump of the oil supply system of the pump shown in Fig. 1, viewed in the axial direction, and Fig. 4 is a partial sectional view taken along the - line of the pump impeller shown in Fig. 3. , Figure 5 is the first
6 is a partial sectional view in the axial direction of the pump similar to the figure, but showing the opposite side of the supply pump and lubricating oil chamber in which the heat exchanger is incorporated; FIG. 6 shows the vicinity of the lubricating oil supply chamber including the heat exchanger 5 is a sectional view of the engine of the present invention taken along the line - in FIG. 5; FIG. In the figure, 10 is a drive device, 12 is a main pump, 20
is a piston, 22 is a sealing tube, 24 is a working chamber, 25 is a cylinder, 30 is a plunger, 3
5 is a side chamber, 42 is an intermediate chamber, 45 is a throttle channel, 1
00 is the oil supply pump, 105 is the reflux pump, 110
120 is a recovery chamber, 150 is a supply pump, and 210 is a heat exchanger.

Claims (1)

[Scope of Claims] 1. At least one piston/cylinder assembly forming a pulsating chamber, a lubricating oil chamber containing lubricating oil, and an oil supply pump supplying lubricating oil from the oil chamber to the piston/cylinder assembly. , a forced circulation oil supply system consisting of a closed circuit including a recovery chamber into which the lubricating oil that has acted on the piston-cylinder assembly is introduced, and a reflux pump that returns the lubricating oil from the recovery chamber to the oil chamber, and the lubricating oil chamber , the oil supply pump, the recovery chamber, and the reflux pump are formed in a housing common to the piston-cylinder assembly, and the lubricating oil chamber surrounds the rotational axis of the drive device of the assembly and has an annular shape concentric with the axis. A lubricating device for the piston/cylinder assembly. 2. The lubricating device according to claim 1, wherein the flow path connecting the reflux pump and the lubricating oil chamber opens at the top of the oil chamber. 3. The lubricating device according to claim 1 or 2, wherein the piston/cylinder assembly has a star-shaped multi-cylinder configuration in which a plurality of piston/cylinder assemblies are arranged around the outer periphery of the drive device. 4. The lubricating device according to claim 1, wherein an overflow passage is interposed between the lubricating oil chamber and the recovery chamber for introducing the lubricating oil in the oil chamber into the recovery chamber. 5. At least one piston/cylinder assembly forming a pulsating chamber, a working medium supply means for supplying a working medium to the assembly, a lubricating oil chamber, and supplying lubricating oil from the oil chamber to the assembly. a forced circulation oil supply system, the lubricating oil chamber is formed in a housing common to the piston-cylinder assembly, and has an annular shape that surrounds and is concentric with the rotation axis of the drive device of the assembly. , the forced circulation oil supply system includes a lubricating oil cooling device, and the cooling device disposes a heat exchanger in the lubricating oil chamber through which a part of the working medium passes. Lubrication device. 6. The flow passage system of the heat exchanger includes at least two communicating parts arranged to sandwich the diameter of the lubricating oil chamber from each other, one communicating part serving as an inlet flow distributor, and the other communicating part serving as a discharge flow distributor. Claim 5, wherein a plurality of heat exchange elements each configured as a tributator and arranged in parallel to each other run in an arc shape from the inlet flow distributor to the discharge flow distributor in both semicircular directions. Lubrication device.